Pressure regulator



Jan. l2, 1943. w. M. WHITE PREssUREREGULAToR 2 Sheets-Sheetv l FiledJune 13, 1940 7'0 C20-SE TURB INE l A\\\\\\\\\\\\\\\\\\\\\m` Jan. 12,1943. W M WH||E PRESSURE REGULATOR Filed June 13, 1940 2 Sheets-Sheet 2Patented Jan. l2, 1943 are sra moans n PRESSURE REGULATOR William M.W'hite, Milwaukee, Wis.

Application .Func 13, 1940, Serial No. 340,315

Claims. (Cl. 137-53) This invention relates to improvements in reliefvalves for discharging large quantities of uid under high pressure andparticularly to such valves as are usually designated as pressureregulators and are employed-in hydraulic power installations. l

The flow of large masses of water involvedin a hydraulic powerinstallation, particularly when reaction type turbines are used andwhenthe installation operates under high heads which produce high velocitiesof ow, cannot be suddenly varied or interrupted without producingpressure waves of such magnitudes as would distort or destroy thevarious water conduits in which the flow is taking place. Variations oreven interruptions of the water flow through a turbine however takeplace even during normal operation of an installation thus making itnecessary to provide a special relief valve which will bypass wateraround the turbine upon operations of such valve in response to turbineoperation causing pressure variations, and hence will regulate the totalpressure in the water conduits within predetermined limits. Suchpressure regulators are combinations of several devices including therelief valve, the means for operating the relief valve under the variousconditions which may arise and the means for harmlessly converting theenergy inherent in the discharge of large quantities of water at highvelocity, to such forms as will not be dangerous or destructive upondischarge. The present hydraulic power developments employing reactionturbines and operating under hydraulic heads up to 500 feet have shownthat the pressure regulators as heretofore constructed are not adequatefor such installations. It has been found particularly that theoperating means for the pressure regulating or relief valve must bemodified to allow only relatively slow movement between the turbine gateshifting ring and the pressure relief valve if the operating means forthe valve fails to function normally, that manually operable means mustbe provided for controlling the movement of the pressure regulatingvalve whenever desired and that means for absorbing the energy inherentin the discharged Water must be radically changed to eliminate the noiseand vibration now encountered in the operation of pressure regulatorsunder high load or high head.

It is therefore an object of the present invention to provide a pressureregulator for hydraulic power installations in which only relativelyslow movement is permitted between the pressure relief valve and themeans for operating the valve if such operating means fail to functionnormally. s

Another object of the invention is to provide a pressure regulator forhydraulic power installations in which a normally power operated meansfor actuating the relief valve may be superseded by means which aremanually operable whenever the operating conditions of the installationwarrant such manual action.

Another object of the invention is to provide a pressure regulator forhydraulic power installations in which air is supplied to thedischarging water at the points of highest velocity and lowest pressureadjacent the relief valve and throughout the chamber immediately belowthe valve to prevent the formation of unstable vacua.

Another object of the invention is to provide an energy absorber incombination with a pressure relief valve in which stable hydraulicconditions are produced to avoid the occurrence of noise and vibrationupon the operation of the pressure regulator.

Another object of the invention is to provide an energy absorber whichwill divide the large mass of discharged water into a plurality ofrelatively small streams from which the energy is separately abstracted.

Another object of the invention is to provide an energy absorber inwhich the discharging water is divided into a plurality of relativelysmall high velocity jets discharging into a large body of water movingat a relatively low velocity.

Another object of the invention is to provide an energy absorber inwhich large masses of water discharge is subdivided into a plurality ofrelatively small jets produced in opposing pairs impinging on each othersubstantially without interference from each other.

Objects and advantages other than those above set forth will be apparentfrom the following description when read in connection with theaccompanying drawings, in which:

Fig. 1 is a verticalpartially sectional view taken on the plane I-I ofFig. 2, of a pressure regulator embodying the improved operating means,the manual control for the operating means, the means for maintainingstable hydraulic conditions about the pressure regulator and the energyabsorber of the present invention;

Fig. 2 is a cross 'sectional view looking down on a horizontal planetaken on the line II-II of Fig. 1 to illustrate the structure of theenergy absorber by which the water passing therethrough is divided intoa plurality of relatively small jets and by which `air is supplied tothe body of the water being discharged to prevent the formation ofunstable vacua;

Fig. 3 is a plan View looking upwardly in the direction of the arrow IIIof Fig. 1 to further illustrate the assembled construction of thevarious parts making up the energy absorber and air supplying meansshown in Figs. 1 and 2;

Fig. 4 is a partially sectional view taken on the plane IV-IV of Fig. 2to illustrate particularly the curvature of one of the jet formingportions of the energy absorber and a portion of the means for supplyingair to such jet;

Fig. 5 is a partial sectional View taken on the plane V-V of Fig. 2 toillustrate the curvature of another of the jet forming portions of theenergy absorber and a portion of the means for supplying air thereto;

Fig. 6 is a partial sectional view taken on the plane VI-VI of Fig. 2 toillustrate the curvature of still another of the jet forming portions ofthe energy absorber and a portion of the means for supplying airthereto;

Fig. 7 is a partial vertical sectional view taken on the plane VII-VIIof Fig. l to illustrate that portion of the entire structure by whichair is conducted to immediately below and about the discharge edges ofthe pressure regulating valve itself;

Fig. 8 is a View taken on the plane VIII-VIII of Fig. 1 to show thatportion of the structure by which air is admitted from an externalsupply pipe to a conduit conveying air to the central portion of theregulator structure and from thence about the edges of the relief valveitself; and

Fig. 9 is a partial vertical sectional view taken on the plane IX-IX ofFig. 2 to illustrate the structure by which air is supplied to theseveral portions into which the discharged annular jet is divided and tothe discharge casing portion below the valve of the pressure regulator.

The structure disclosed in the present application consists essentiallyof a relief valve, the valve operating and control devices, and meansfor producing stable hydraulic conditions in the structure and the meansfor absorbing the major portion of the energy in the fluid dischargedthrough the relief valve.

Referring to the drawings by reference numerals, numeral I6 designates aconduit connected with a source of high pressure fluid in largequantities, such as a penstock or the spiral casing of a hydraulicturbine and in which the iluid flow is subject to rapid variations or tointerruption. One end of the conduit I6 is connected with the valvecasing I1 shaped substantially as a pipe elbow with the dischargeportion thereof directed downwardly and provided with a seat for a valveI8. The valve I8 is preferably substantially formed as a somewhatconical shaped disk thus producing an annular discharge of iluid aboutthe edges thereof and is mounted on a stem I9 extending from both sidesof the valve and guided in its vertical movement by structures mountedin or attached to a portion of the valve casing. The upper end of theValve stem I9 extends through a conical guiding and partitioning member2| mounted in the valve casing I1 and closing off one end of acylindrical extension 22 from'the upper portion of the casing. Thecasing extension 22 is provided for a portion of its length with acylindrical liner 23 and is closed by a top cover or head 24. The upperend of the valve stem I 9 has mountedA thereon a hollow extension 25which forms a support for a piston 21 tting into the cylinder liner 23and movable therein. The cylindrical casing extension 22 and the liner23 form the cylinder of a servomotor with its piston 21 mounted on theValve stem for closing the valve upon movement of the piston in responseto the admission of iluid pressure to the chamber formed by the cylinderbelow the piston surfaces. The valve I8 opens downwardly and, beingsubject to the pressure of the fluid to be discharged, the valve isself-opening and the servomotor 22, 23, 21 is required only to raise thevalve I8 to closed position.

The Valve stern extension 26 is flanged at the upper end thereof toengage between the anges 'of a coupling 3| which flanges are spaced agreater distance than the thickness of the flange on lthe Vextension 26thus providing a lost motion connection under the action of acompression spring 32 acting between the end of the valve stem I9 andthe end of coupling 3 I. The coupling 3l connects with a cylinder 33movably mounted in the servomotor cylinder head 24 and extendingupwardly therefrom. The cylinder 33 receives a piston 34 provided withthe usual valves 35 and 36 controlling the flow of uid through thepiston and which valves are preferably adjustable as is well known. Thecylinder 33 and the piston 34 together form a dashpot 'of which bothelements are movable. The dashpot piston 34 is provided with a rod 38extending upwardly through the dashpot cylinder 'head 31 and pivotallyconnected with one end of a rod 4I having the other end connected withone arm of a bell crank 42 mounted on the servomotor cylinder head 24.'Ihe other arm of the bell crank 42 is connected with a push rod 43which is in turn connected with 'means responsive to or related to thepressure variations or to flow interruption in the conduit I6 such asare caused by movement of the shifting ring or governor of a hydraulicturbine (not shown).

The application of uid pressure from a suitable source such as theconduit I6, to the lower chamber of Athe servomotor 22, 21 to move thevalve I8 to closed position and the discharge of pressure from suchchamber to allow the valve I8 to open, are controlled by a control orpilot valve including the Vvalve casing 46 connected with and mounted onthe lower servomotor chamber. Fluid pressure is supplied through a port41 and is discharged through a'port 48 of the valve casing under thecontrol of a valve v49 having a piston 50 mounted on the Valve stem 52and operating in a cylindrical portion of the valve casing 46 under theaction of pressure for operating the servomotor, to counterbalance the nweight ofthe valve. The chamber above the piston 53 is vented to thevalve discharge by a pipe 5I. The upper end of the stem 52 of thecontrol valve 43 is provided with a lost motion connection comprising acompression spring 56 in a housing 51 and acted on by a plunger 58having the upper end connected with one end of a lever 6I pivot-ed atthe other end on the dashpot cylinder 33. A rod 62 is xedly mounted onthe servomotor piston 21 and extends upwardly through the servomotorcylinder head 24. The upper end of the rod 62 is connected with one endof a lever 63 having the other end -thereof connected with a link 64pivoted to a fixed point on the control valve casing 46. A substantiallycentral point of the lever 63 is connected with `a substantially central.point of the lever 6I by a link 65. A rotatable screw 66 is pivotallymounted at a point on the control valve casing 46 andv bears a nut B1 onwhich is mounted a lever 68 pivotally connected with the control valvestem 52 and having its other end connected by a link 69 with the lever63. .The leverage 6I to 65 inclusive provides means for operating thecontrol valve 49 responsive to movement of the dashpot cylinder 36 andalso restores the control valve 49 to the discharge or closed positionupon movement of the servomotor piston 2l. The leverage S6 to 69inclusive provides a manually operable means for operating the controlvalve 48 which controls the servomotor 22, 2l regardless of the positionof the relief valve I8 or of the operating servomotor and controldashpot and valve above described.

When the relief valve i8 is opened to discharge high pressure water fromthe conduit |5, the high pressure is converted into high velocity in anannular jet about the edge of the disk I8. Such high velocity producesunstable vacua immediately adjacent the valve I3 which vacua form andcollapse at a relatively high frequency toproduce vibrations as well asa cracking or pounding noise, both of which effects are disturbing andare evidence of conditions which may be dangerous or even destructive.Such effects may be eliminated by the introduction of compressed airabout the edge of the Valve I8 which is therefore preferably formed witha hollowed out lower side enclosed by a plate 1| having channels formedadjacent the outer edge thereof to cooperate with the edge portion ofthe valve disk i3 to form air distribution nozzles about the edge of thevalve. The lower end of the valve stern i9 is bored out to provide apassageway 12 which is connected with the chamber formed between thevalve 3 and the plate 'll and is movably guided in the central portion14 of a spider having four splitter arms l5, 755, Ti, I8 mounted in thelower casing portion 'F9 attached to the valve casing Il. The severalsplitter arms l5, l5, 'll and T3 are made substantially triangular andextend entirely across the casing portion '."9 thus dividing theinterior ofy such casing and also the discharge fluid passingtherethrough, into four portions. The spider arm splitters 15 and i3 areconnected by apertures as at 8| and S2 with the central spider portionld and serve as conduits for compressed air flowing from a manifold 83extending partially around the casing portion 'E9 and connected byapertures as at 84. with the spider arm splitters "E and 18. Compressedair is supplied to the manifold 83 from a suitable source by a pipe 85.

IThe spider arm splitters 'It and l1 are each provided with a series ofapertures 8l, |38 in the sides and apertures 89 in the bases of sucharms and are connected by apertures 9| with a manifold 92 extendingpartially around the casing portion 'i9 and supplying compressed airfroma suitable source by way of the pipe 93. It will be seen that theapertures 81, 88 are formed in the sides of the spider arm at the pointat which the highest Velocity of iluid flow is present and that theapertures 89 are located adjacent the edges from which the fluid isdischarged from the splitter arms into the casing portion 79. Airsupplied by way of the three series of apertures above described istherefore admitted at the points at which the lowest pressures andhighest velocities are present thus preventing the formation of vacua atsuch points.

The space in each of the four portions dened by adjacent spider armssuch as that between the spider splitter arms 'l5 and 1l, is partiallylled shaped portions of the annular discharge jet flowing between thesplitters 15 and "El, into a plurality of jets deflected at differentangles across the casing 19, each jet being only a relatively smallfraction of the entire mass of water discharged. Each such structurecomprises a plurality of splitters 9B, 97, 98 and Se spaced from eachother by approximately one-fifth of the length of the arc of thequadrant. The central three spaces between the splitters such as spacesbetween the splitters 96 and Ell, 91 and Sil, and 98 and 99 are providedwith deflectors as at lili, itt and |63 which are curved on radiidiffering from each other and from the inner surface of the casingportion i9 and are held in position by supports HB5, |66 and |01 betweenthe casing portion i9 and such deflectors. Due to the differentcurvature of the several deiiectors between the pairs of splitters, thewater flowing between each of such pairs of splitters is dischargedtherefrom at an angle dependent on the curvature of the deilector. Itwill be seen that each of the four quadrants into which thecasingportion 19 is divided by the splitting spider above described isprovided with all of the constructions such as has been describedimmediately above, which are arranged to provide opposing pairs of jetsin each of two of the quadrant portions.

The spaces dened by the splitters, the deflectors and the deflectorsupports communicate by way of apertures as at |98 through the deflectorsupport |05 with the interior of the casing portion 19 and withapertures as at |69 through the wall of the casing portion 19 tocommunicate with the manifold 92 to supply air at the discharge edge ofthe deilectors to prevent the formation and collapse of unstable vacuaat such locations. The several jet deilecting structures are similar toeach other and are similarly placed so that pairs of jets in opposingquadrants and on diameters through the casing will meet and oppose eachother at some point within the cas- Aing. It will be understood ofcourse that such meeting and opposing of the jets occurs only ii thecurvatures of the deilectors are so chosen that the jets do notsubstantially interfere with each other. It will be further understoodthat the outside jets in each quadrant which flow in contact with theinner surface of the casing portion T9 are not intended to meet and.oppose each other within such casing portion. In any event the severaljets are discharged into a large rela-V tively slowly moving mass ofWater in. which the energy of the discharge is dissipated in turbulence.It will be understood that the water splitting and jet deectingstructure above described can be applied t0 structures other than therelief valve shown to absorb the energy in a now of high velocity waterin large masses.

All of the water is discharged from the casing portion 79 into adischarge conduit of substantially greater cross sectional area than thecasing portion for the purpose of further dissiplating energy and toreduce the turbelence in the discharge water. Such sudden increase inarea in a conduit having a flow of water therethrough however producesregions in which unstable vacua may form. A sheet -metal ring H2 istherefore so placed at the junction of the casing F9 and the conduit asto form a channel to which compressed air is supplied by a pipe I3 andfrom which such air is discharged through several series of aperturesshown at ||4 and H5. Air is thus distributed entirely around the pebysimilar structures subdividing the quadrant riphery of the dischargeconduit and prevents the formation of unstable vacua adjacent suchperiphery. y

As long as the conditions of operation of the turbine or other deviceconnected with the conduit I6 do not change, the speed governor or otheractuating device for the operating rod 43 does not operate and thepressure regulator remains in the position shown in which the dashpotpressures are balanced and the control valve 49 admits pressure belowthe servomotor 23 and 21 to hold the relief valve I8 in the raisedposition against its seat. If a gradual change of condition takes placewhich causes gradual movement of the rod 43, such movement istransmitted through the crank 42 and the rod 4I to the dashpot piston34. If the rate of change of dashpot piston position is not beyond therate at which dashpot pressures remain balanced by now of uid throughthe dashpot piston valve 35 and 35, the position of the dashpot cylinderwill remain unchanged and the control valve 43 will remain intheposition shown thus retaining the servomotor piston 21 and the reliefvvalve I8 in the position shown.

However if a sudden change takes place in the operating conditions ofthe turbine such as rapid closure of the turbine gate, the usual speedgovernor moves rod 43 rapidly toward the right and causes a highpressure to be exerted on the dashpot piston 34. The dashpot pistonvalves 35 and 35 limit the rate at which fluid can pass from be low thedashpot piston to above such piston and a pressure is therefore producedin the dashpot cylinder 33 which moves such 'cylinder downwardly untilthe play between the flanges of coupling 3| and the flanged end of thevalve stern extension 26 is taken up thereby compressing spring 32. Suchdownward movement of the dashpot cylinder 33 rocks lever 6i about link85 as a fulcrum and pulls the control valve stem 52 upwardly to move thecontrol valve 49 into position to shut off the supply of pressurethrough the passageway 41 and to open the discharge passageway 49.Continued downward pressure of the dashpot cylinder 33 added to thehydraulic head j acting on the relief valve causes opening of such thespring 32 expands and raises the dashpot cyli inder 33 at the rate atwhich uid flows through the dashpot valves 35 and 36. Such raising oithe dashpot cylinder 33 tilts the lever 6I about the link 65 as afulcrum to cause the plunger 58 to compress the spring 55 in the controlvalve stem 52 which presses the control valve 49 on its lower seat asshown. Pressure is then again admitted through the passageway 41 intothe servomotor cylinder 22 below the servomotor piston 21 which raisesthe valve I8 to the closed position shown. Rising 0f the servomotorpiston 21 movesthe rod 52 upwardly and tilts the lever 63 about the endof link 64 as a pivot thus raising link 85 yand lever 6I to relieve thecompression of a spring 55 in the control valve stem 52. Pressure actingthrough the passageway 41 of the control valve on the piston 58 justbalances the weight of the control valve 49 and its stem 52 so that thepressure acting on the control valve 49 retains the valve in theposition shown at which pressure is admitted tothe servomotor 22.

If conditions occur which make it desirable to open the lrelief valve I8without requiring that such conditions affect the movement of the rod43, the control valve 49 can be raised by rotating screw 66 in adirection to move the nut 61 upwardly which moves the attached end ofthe lever 68 upwardly against the compression of spring 56. The supplyof pressure below the servomotor piston 21 is then shut o andthedischarge passageway 48 through the control valve is open. The vreliefvalve I8 then opens due to the fluid pressure acting thereon and at arate dependent upon the passage of fluid to the dashpot valve 35 and 38.Downward movement of the servomotor piston 21 moves rod 62 down to tiltlever 63 about the end of link 65 which moves upwardly on the link 89and tends to raise the control valve stem 52 higher. If the controlvalve 49 is already at the limit of its stroke, such tendency merelyfurther compresses spring 56. Closure of the control valve 49 isobtained by reverse rotation of the screw 66 to reverse the abovedescribed sequence of operations.

When the relief valve I8 is open, water is discharged all about theperiphery thereof in an annular jet at high velocity which producesunstable vacua adjacent the casing 19 and in the space under the valve.The production and collapse of such vacua adjacent the valve I8, areeliminated in large measure by the supply of compressed air through thepipe 85, manifold 33, splitter arms 15 and 18 and through the passage inthe valve stem to the chamber formed by the valve disk I8 and the plate1I, from which the air is discharged through the nozzles at the edge ofthe disk by its pressure and also as a result of the aspirating effectof the high velocity water iiow over the edge of the valve disk. Theannular jet discharged about the edge of the disk is divided into fourparts by the spider arms 15, 16, 11 and 18 and is further aerated bycompressed air supplied through the pipe 93, manifold 92, spider arm 1Band 11 and discharged through the apertures 81 and 88 in the sides andthe apertures 89 in the bottoms of both of such spider arms.

Each of the four portions into which the annular jet is divided by thespider arms, is further subdivided into five jets by splitters 95, 91,98 and 99. Two jets of each quadrant flow outwardly from the axis of thestructure along the inner surface of the casing 19 while the remainingthree jets iiow over the several deecting surfaces IDI, |02 and I 93which direct such jets at different angles such that the jets flowingover deflectors |02 at least would meet substantially centrally in thedischarge conduit III. The tendency of the jets to form unstable vacuais restricted by the admission of air adjacent to the points Aat whichthe jets leave the deecting surfaces. It will be understood that thespider arms and the deflecting structures break up the mass of theannular jet discharged, into a plurality of jets which discharge into amass of relatively slow moving Water in the discharge conduit, that suchmass of water is kept in a state of turbulence which dissipates theenergy of the jets discharged thereinto and that air is admitted atvarious points throughout the energy absorber structure to prevent theextensive formation and collapse of unstable vacua.

Although but one embodiment of the present invention has beenillustrated and described it will be apparent to those skilled in theart that various changes and modications may be made therein withoutdeparting from the spirit of the invention or from the scope of theappended claims.

It is claimed and desired to secure by Letters Patent:

l. In a regulator for limiting the pressure variations in the now offiuid in a conduit, a power operated relief valve, means for controllingthe application of power for operating said valve, means forautomatically actuating said control means responsive to conditionscausing pressure variations, means for restoring said control means toneutral position after automatic actuation thereof, and means formanually actuating said control means and operating upon movement ofsaid valve for restoring said control means to neutral position aftermanual actuation thereof.

2. In a regulator for limiting the pressure variations in the ow offluid in a conduit, a power operated relief valve, means for controllingthe application of power for operating said valve, means forautomatically actuating said control means responsive to conditionscausing pressure variations, a leverage interconnecting said valve, saidcontrol means and said control actuating means for restoring saidcontrol means to neutral position after automatic actuation thereof, alink connected with said leverage, and a lever connected with said link,said link and said lever cooperating in manual operation of said controlmeans and in automatically restoring said control means to neutral aftereach manual actuation thereof.

3. In a regulator for limiting the pressure variations in the flow offluid in a conduit, a pressure operated relief valve, a valvecontrolling the application of pressure for operating said relief valve,means including a dash pot for automatically actuating said controlvalve responsive to conditions causing pressure variations, a leverageinterconnecting said relief valve and said control valve and said dashpot for restoring said control valve to neutral position after eachactuation thereof, a link connected with said leverage, and a leverconnected with said link, said link and said lever cooperating in manualoperation of said control valve and in automatically restoring saidcontrol valve to neutral after each manual actuation thereof.

4. In a regulator for limiting the pressure variations in the flow ofliquid in a conduit, a power operated valve arranged in the conduit fordischarging an annular jet, means for supplying air at the periphery ofsaid valve and interiorly of the annular jet, and means for distributingair throughout the liquid after discharge from said valve, the supply ofair preventing the formation of unstable vacua adjacent said valve andin the conduit portion receiving the discharge from said valve.

5. In a regulator for limiting the pressure vari ations in the flow ofliquid in a conduit, a power operated valve of the disk type arranged inthe conduit and having a hollow stem, the disk of said valve forming achamber with apertures at the periphery thereof and the hollow stem ofsaid valve forming a passage for air to the chamber within the disk, aplurality of perforated conduits extending across the liquid conduit inthe discharge from said valve for distributing air throughout the liquiddischarge from said valve, and means for supplying air to the stem ofsaid valve and to said conduits, the supply of air preventing theformation of unstable vacua adjacent said valve and in the conduitportion receiving the discharge from said valve.

WILLIAM M. WHITE.

